EP3045769B1 - Damper device - Google Patents

Damper device Download PDF

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Publication number
EP3045769B1
EP3045769B1 EP13893555.6A EP13893555A EP3045769B1 EP 3045769 B1 EP3045769 B1 EP 3045769B1 EP 13893555 A EP13893555 A EP 13893555A EP 3045769 B1 EP3045769 B1 EP 3045769B1
Authority
EP
European Patent Office
Prior art keywords
spring
metallic core
seat
coil springs
outer diameter
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP13893555.6A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3045769A1 (en
EP3045769A4 (en
Inventor
Hiroki Uehara
Yuuzou Akasaka
Makoto Ogata
Tomoharu Fujii
Yoshinari Yoshimura
Takeshi Senoue
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Exedy Corp
Nissan Motor Co Ltd
Original Assignee
Exedy Corp
Nissan Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Exedy Corp, Nissan Motor Co Ltd filed Critical Exedy Corp
Publication of EP3045769A1 publication Critical patent/EP3045769A1/en
Publication of EP3045769A4 publication Critical patent/EP3045769A4/en
Application granted granted Critical
Publication of EP3045769B1 publication Critical patent/EP3045769B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/64—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts
    • F16D3/66—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts the elements being metallic, e.g. in the form of coils
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs
    • F16F1/12—Attachments or mountings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/1343—Wound springs characterised by the spring mounting
    • F16F15/13438—End-caps for springs
    • F16F15/13446—End-caps for springs having internal abutment means

Definitions

  • the present invention relates to a damper device, provided to a drive transmission system or the like of a vehicle, and comprising a spring seat that supports a coil spring which absorbs a torsional vibration.
  • a plurality of coil springs are interposed between a first rotating body and a second rotating body in the circumferential direction, and the two ends of each coil spring are seated on the rotating bodies via a spring seat.
  • a coil spring with a relatively high rigidity is used so that even if a centrifugal force is applied during a rotation of the rotating body, the deformation in the device outer diameter direction is less likely to occur, and so that the deformation is regulated by an overhang portion of the spring seat.
  • the deformation amount of the coil spring in the device outer diameter direction during a rotation of the rotating bodies becomes relatively large.
  • the contact angle between the seat portion and the end of the coil spring is changed, generating rubbing between the two.
  • an object of the present invention is to provide a damper device capable of achieving a suppression of the wear in the seat portion of the resin spring seat.
  • a metallic core exposed portion in which a seat portion metallic core member is exposed so as to be contactable with a coil spring, is provided on a portion of the spring seating surface which slides against a coil spring. Accordingly, the wear of the resin portion of the spring seating surface during the deformation of the coil spring can be suppressed, compared to one that is not provided with a metallic core exposed portion.
  • the seat portion metallic core member is not covered by the resin in the portions on the spring seating surface other than the metallic core exposed portion, it is possible to suppress the friction resistance between the coil spring and the spring seat during relative movement to improve durability.
  • Figure 1 is a cross-sectional view of the damper device A
  • Figure 2 is an exploded perspective view of the damper device A
  • Figure 3 is a cross-sectional view illustrating the main parts of the damper device A.
  • the damper device A is a mechanism for transmitting the torque as well as for absorbing and damping the torsional vibration, and is provided on a drive power transmission path between a motor Mot and an engine Eng, which are not shown, in the present first embodiment. That is, while not shown, the damper device A is provided to the drive power transmission system of a hybrid vehicle. Then, when driving the engine Eng, transmitting the engine drive force to the motor Mot side and generating the power, etc., and further, transmitting the engine drive force to the unillustrated drive wheel side via the motor Mot, etc., are possible. In addition, the engine can be started by inputting the drive force of the motor Mot to the engine Eng, when the engine Eng is not being driven. At the time of this type of drive transmission, the damper device A mainly carries out absorption and damping of torsional vibration that is generated with the driving of the engine Eng.
  • the damper device A comprises a hub plate (first rotating body) 1 that is connected to the motor Mot so as to be inputtable and outputtable, and an input-output plate (second rotating body) 2 that is connected to the engine Eng so as to be inputtable and outputtable, as illustrated in Figure 1 and Figure 2 .
  • a hub plate (first rotating body) 1 that is connected to the motor Mot so as to be inputtable and outputtable
  • an input-output plate (second rotating body) 2 that is connected to the engine Eng so as to be inputtable and outputtable, as illustrated in Figure 1 and Figure 2 .
  • three pairs of a first coil spring 31 and a second coil spring 32 are interposed between the two plates 1 and 2 in the circumferential direction. That is, along with the hub plate 1 and the input-output plate 2 moving relatively in the circumferential direction, one of the first coil spring 31 and the second coil spring 32 is compressed while the other is stretched.
  • the torsional vibration that is inputted to the hub plate 1 and the input-output plate 2 is absorbed and damped by the elastic deformation of these coil springs 31 and 32.
  • a clutch which connects and disconnects the transmission of the drive force may be provided between the hub plate 1 and the unillustrated motor Mot.
  • a second plate 22 is fixed to the input-output plate 2 by a plurality of rivets 21 sandwiching an intermediate plate 23 therebetween, on the motor side in the axial direction of the damper device A, and in the arrow Ce direction in Figure 1 and Figure 2 (this direction is hereinafter referred to as the device axial direction). Then, three pairs of housing windows 2a and 22a which house the pairs of coil springs 31 and 32 in the circumferential direction are extended on the input-output plate 2 and on the second plate 22 in the circumferential direction.
  • Connecting portions 2b which connect the inside and outside in the device radial direction (the radial direction of the damper device A; the arrow OUT indicates the outer diameter direction) are provided between the housing windows 2a of the input-output plate 2 in the circumferential direction.
  • connecting portions 22b which connect the inside and outside in the device radial direction are provided between the housing windows 22a of the second plate 22 in the circumferential direction.
  • each of the intermediate plate-side support arms 24 is disposed in an intermediate portion of the housing windows 2a and 22a in the circumferential direction.
  • a gear member 25 for starting the engine is joined to the outer perimeter of the input-output plate 2 by a plurality of rivets 21.
  • the second plate 22, the intermediate plate 23, and the gear member 25 are integrally rotated with the input-output plate 2.
  • Three hub plate-side support arms 11 which extend in the outer diameter direction are provided to the hub plate 1, at regular intervals in the circumferential direction, in the same way as the intermediate plate 23. These hub plate-side support arms 11 are disposed in positions between the housing windows 2a and 22a, in the circumferential direction. Thus, the hub plate-side support arms 11 and the intermediate plate-side support arms 24 are alternately arranged in the circumferential direction.
  • the intermediate plate-side support arms 24 of the intermediate plate 23 and the hub plate-side support arms 11 of the hub plate 1 are relatively movable in the circumferential direction, and the two coil springs 31 and 32 described above are interposed between the support arms 11 and 24 in the circumferential direction.
  • Both of the coil springs 31 and 32 are alternately disposed between both the support arms 11 and 24 in the circumferential direction, and when one set from among the set of the three first coil springs 31 and the set of the three second coil springs 32 is compressed in parallel, the other set is stretched in parallel, as illustrated in Figure 3 .
  • Both of the coil springs 31 and 32 are respectively attached to the hub plate-side support arms 11 via a first spring seat 41, and attached to the intermediate plate-side support arms 24 via the second spring seat 42.
  • the two spring seats 41 and 42 are formed by carrying out a molding in which a metallic core member 45, described below, is covered by a resin with a low friction resistance, and comprise a seat portion 43 and an overhang portion 44, respectively, as illustrated in Figure 4A and Figure 4B .
  • the seat portion 43 is for supporting the ends of the two coil springs 31 and 32 in the spring central axis Sc direction, and is formed in a substantially disc shape, as illustrated in Figure 5 .
  • a guide protrusion 43c which is inserted in the inner perimeter of the ends of the coil springs 31 and 32 to restrict the movement of the coil springs 31 and 32 in the radial direction, is formed projecting from the radial direction center of the spring seating surface 43a, on which are seated the coil springs 31 and 32.
  • the overhang portion 44 is formed along the outer perimeter part of the seat portion 43, extended in the axial direction from an area of substantially half the portion on the device outer diameter direction (the arrow OUT direction in Figure 3 ) side. This overhang portion 44 is for suppressing the coil springs 31 and 32 from deforming in the damper outer diameter direction due to the centrifugal force during a rotation of the damper device A, and is formed so as to cover the device outer diameter direction side of the coil springs 31 and 32.
  • ribs 44a and 44b and 44b are provided in three locations, in the circumferential direction center and the two circumferential ends, of the overhang portion 44, extending in the axial direction (along the spring central axis Sc direction, illustrated by the dashed-dotted line in Figure 5 ), as illustrated in Figure 5 .
  • the metallic core member 45 is formed of a thin metal plate, and a seat portion metallic core member 451, an overhang portion metallic core member 452, and side edge reinforcement arm portions 453 and 453 are formed integrally, as illustrated in Figure 5 .
  • the seat portion metallic core member 451 is embedded in the seat portion 43, and is formed in a disc shape that is smaller in diameter than the seat portion 43.
  • the overhang portion metallic core member 452 is the top portion of the overhang portion 44 in the device outer diameter direction, and is disposed inside of the rib 44a.
  • the side edge reinforcement arm portion 453 is disposed along the rib 44b on the two circumferential ends of the arc of the overhang portion 44, and is formed in a rod shape that is narrower in width than the overhang portion metallic core member 452.
  • the overhang portion metallic core member 452 comprises a low-rigidity portion 452a on the side close to the seat portion 43, and a high-rigidity portion 452b on the side far from the seat portion 43, on the distal end side of the overhang portion 44.
  • the difference in the rigidity between the low-rigidity portion 452a and the high-rigidity portion 452b is set by the difference in the width of the metal plate member that forms the overhang portion metallic core member 452, where the high-rigidity portion 452b is formed wider than the low-rigidity portion 452a.
  • the overhang portion metallic core member 452 is formed in a T-shape in the plan view, as illustrated in Figure 6 .
  • the dimension L1 of the low-rigidity portion 452a in the protruding direction of the overhang portion is formed to be larger in dimension than the axial direction dimension L2 of the guide protrusion 43c. Therefore, the low-rigidity portion 452a is provided to a side position of the overhang portion 44 that is further in the distal direction than the distal end of the guide protrusion 43c, in the circumferential direction. Additionally, the high-rigidity portion 452b is provided to a position of the overhang portion 44 that is further on the distal end side than the distal end of the guide protrusion 43c, in the circumferential direction.
  • the overhang portion metallic core member 452 is exposed in the device inner diameter direction (direction opposite of the arrow OUT) with respect to the resin material that forms the overhang portion 44.
  • the side edge reinforcement arm portion 453 is entirely embedded with respect to the resin material that forms the overhang portion 44, as illustrated in Figure 5 .
  • a metallic core exposed portion 451a in which the seat portion metallic core member 451 is exposed so as to be contactable with the coil springs 31 and 32, is provided to the portion of the spring seating surface 43a that comes in contact with the coil springs 31 and 32, as illustrated in Figure 5 .
  • this metallic core exposed portion 451a is provided to a site on the spring seating surface 43a that comes in strong contact with the coil springs 31 and 32. That is, the metallic core exposed portion 451a is disposed further on the device inner diameter direction (the direction opposite of the arrow OUT illustrated in Figure 4A, Figure 4B ) side position than the spring central axis Sc of the coil springs 31 and 32 on the spring seating surface 43a.
  • the metallic core exposed portion 451a is provided in a semicircular arc shape along a wound-shape circumferential portion of the spring seating surface 43a, where the ends of the coil springs 31 and 32 are abutted.
  • a region on the spring seating surface 43a that includes the region further on the device outer diameter direction side than the spring central axis Sc, excluding the metallic core exposed portion 451a, is set as the coated region 43b in which the seat portion metallic core member 451 is coated by the resin.
  • a pair of attaching recesses 11a and 24a which are recessed in the circumferential direction, are formed on each of the support arms 11 and 24, so as to allow the housing of the ends of the coil springs 31 and 32 as well as the spring seats 41 and 42.
  • Attaching portions 11b and 24b for attaching the spring seats 41 and 42 are provided to a portion sandwiched by the pair of attaching recesses 11a and 24a, in the circumferential direction.
  • Flanges 1 If and 24f are extended in the circumferential direction on the outer diameter direction side of the attaching recesses 11a and 24a.
  • each of the spring seats 41 and 42 are provided a pair of clamping protrusions 47 and 46 that sandwich the attaching portions 11b and 24b of the support arms 11 and 24 in the axial direction, on the outside surface which is on the opposite side of where the guide protrusion 43c is provided in the seat portion 43.
  • the clamping protrusion 47 provided to the first spring seat 41 is formed in a relatively smaller shape than the clamping protrusion 46 of the second spring seat 42, as illustrated in Figure 4A and Figure 4B .
  • the hub plate-side support arms 11 which are sandwiched by the clamping protrusions 47 are configured so that the connecting portion 2b of the input-output plate 2 and the connecting portion 22b of the second plate 22 are disposed on both sides thereof in the device axial direction (arrow Ce direction), as illustrated in Figure 2 . Therefore, the pair of clamping protrusions 47 sandwich the attaching portion 11b, and are further sandwiched by the connecting portions 2b and 22b, as illustrated in Figure 9 .
  • the attachment strength of the hub plate-side support arms 11 of the first spring seat 41 to the attaching portion 11b can be sufficiently secured even with a relatively small clamping protrusion 47.
  • the connecting portions 2b and 22b do not exist in the axial direction of the intermediate plate-side support arms 24 of the intermediate plate 23, and the second spring seat 42 is attached to the intermediate plate-side support arm 24 only by a pair of clamping protrusions 46. Therefore, the clamping protrusion 46 of the second spring seat 42 is formed to have a relatively larger shape than the clamping protrusion 47 of the first spring seat 41, in order to secure the attachment strength thereof.
  • clamping protrusion 46 of the second spring seat 42 The configuration of the clamping protrusion 46 of the second spring seat 42 will be described in further detail below.
  • the interval between the pair of clamping protrusions 46 and 46 in the device axial direction is configured to be an interval with which sandwiching the attaching portion 24b is possible; by sandwiching the attaching portion 24b in this way, the movement of the second spring seat 42 in the device axial direction (arrow Ce direction) is regulated, as illustrated in Figure 6 .
  • the support is one in which a relative rotation is possible in the device outer diameter direction, which is the arrow R4b direction in Figure 4B , with respect to the attaching portion 24b.
  • the clamping protrusion 46 is formed in a semicircular shape, which is an arc shape along the turning trajectory in the outer diameter direction, when viewed from the device axial direction, as illustrated in Figure 7A .
  • clamping protrusion 46 comprises a low-rigidity portion 46a and a high-rigidity portion 46b.
  • the low-rigidity portion 46a is provided to the clamping protrusion 46 on the side that is close to the overhang portion 44, in a region that is further on the device outer diameter direction side than the spring central axis Sc.
  • the spring central axis Sc of Figure 7A indicates the central axis in a state in which the coil springs 31 and 32 are not deformed in the device outer diameter direction, as illustrated in Figure 4A .
  • This low-rigidity portion 46a is set to a rigidity that can permit the overhang portion 44 to be elastically deformed in the device outer diameter direction and the device axial direction.
  • the high-rigidity portion 46b is formed to be higher in rigidity than the low-rigidity portion 46a by erecting two ribs 46c and 46c on the outer side of the clamping protrusion 46 in the spring central axis Sc direction.
  • these ribs 46c and 46c are provided inclined obliquely with respect to the spring central axis Sc, as illustrated in Figure 7A .
  • This inclination is a direction along an input direction (arrow F direction) from the coil springs 31 and 32, when the coil springs 31 and 32 are displaced in the device outer diameter direction by a centrifugal force.
  • the two ribs 46c and 46c are juxtaposed in the device outer diameter direction and the device inner diameter direction, across the input direction indicated by this arrow F.
  • the two spring seats 41 and 42 are turned in the outer diameter direction due to a backlash, etc., introduced upon the assembly, with respect to the attaching recesses 11a and 24a of the plates 1 and 2 of the support arms 11 and 24.
  • the two spring seats 41 and 42 will try to turn with respect to the plates 1 and 2, in the direction indicated by the arrow R4b in Figure 4B .
  • the elastic deformation occurs in the arrow R4b direction, and the overhang portion 44 is deformed so as to displace the distal end thereof in the outer diameter direction.
  • the seat portion 43 is also elastically deformed outward from the spring with respect to the spring central axis Sc, accompanying the deformation of the overhang portion 44.
  • One location is the device inner diameter direction surface of the overhang portion 44, and the other location is the spring seating surface 43a of the seat portion 43. Countermeasures against wear in the first embodiment will be described below.
  • the two coil springs 31 and 32 contact the inner side surface of the overhang portion 44, when deforming in the device outer diameter direction (arrow OUT direction), as illustrated in Figure 4B .
  • this contact force is strong, friction is generated on the inner side surface of the overhang portion 44 (the device inner diameter direction side surface).
  • the overhang portion 44 exposes the overhang portion metallic core member 452 on the inner perimeter surface of the apex portion in the device outer diameter direction. Accordingly, when deforming in the device outer diameter direction, the coil springs 31 and 32 directly contact the overhang portion metallic core member 452 in the portions that come in strong contact, thereby avoiding friction in the resin portion.
  • the device inner diameter direction side indicated by the circle P comes in stronger contact with the seat portion 43 than the device outer diameter direction side at the two ends in the direction along the spring central axis Sc.
  • a semi-circular metallic core exposed portion 451a formed along the arc of the coil springs 31 and 32 is provided to the spring seating surface 43a of the seat portion 43 further on the inner diameter side than the spring central axis Sc. Therefore, even when the coil springs 31 and 32 and the device inner diameter direction of the spring seating surface 43a come in strong contact, the occurrence of wear in the resin can be prevented.
  • the overhang portion metallic core member 452 in addition to providing the above-described overhang portion metallic core member 452 to the overhang portion 44, the overhang portion metallic core member 452 is provided with a high-rigidity portion 452b on the distal end side of the overhang portion 44. Accordingly, excessive deformation of the distal end of the overhang portion 44 is suppressed by the high-rigidity portion 452b and an occurrence of the tip split described above is suppressed.
  • the overhang portion metallic core member 452 is provided with a low-rigidity portion 452a on the side that is close to the seat portion 43. Therefore, compared to when the entire overhang portion metallic core member 452 is configured to be highly rigid to allow suppression of the tip split described above, deformation of the spring seats 41 and 42 in the arrow R4b direction in Figure 4B becomes likely to occur, following a deformation of the coil springs 31 and 32 in the device outer diameter direction. It is thereby possible to ease the input to both the coil springs 31 and 32 and the overhang portion 44 at the time of contact, and to suppress an occurrence of excessive deformation in the coil springs 31 and 32, such as that illustrated in Figure 8 . Therefore, damages, etc., to the coil springs 31 and 32 and the spring seats 41 and 42 can be suppressed to improve durability.
  • the low-rigidity portion 452a is provided to a position that is further on the distal end side of the overhang portion 44 than the distal end of the guide protrusion 43c, as illustrated in Figure 6 .
  • the deformation in the device outer diameter direction is restricted to a certain degree, and the deformation in the device outer diameter direction is more likely to occur on the distal end side of the overhang portion 44 than the guide protrusion 43c.
  • the low-rigidity portion 452a is disposed up to a position that is further on the distal end side of the overhang portion 44 than the distal end position of the guide protrusion 43c, and the high-rigidity portion 452b is disposed further on the distal end side of the overhang portion 44 than the distal end position of the guide protrusion 43c.
  • Deformation of the spring seats 41 and 42 becomes more likely to occur, following the deformation of the coil springs 31, 32 in the device outer diameter direction. Therefore, excessive deformation of the coil springs 31 and 32 such as that illustrated in Figure 8 can be more reliably suppressed, and the damages, etc., to the coil springs 31 and 32 and the spring seats 41 and 42 can be suppressed to improve durability.
  • the intermediate plate 23 Since the intermediate plate 23 is connected to the engine Eng, there are cases in which the intermediate plate receives an input in the axial direction (the arrow Ce direction of Figure 1 and Figure 2 ) caused by the engine vibration, during an input from the engine Eng, as described in Figure 1 .
  • a gear member 25 for starting the engine is provided to the input-output plate 2 while the coil springs 31 and 32 are held, input from the engine Eng is directly transmitted from the input-output plate 2 to the coil springs 31 and 32, which increases this input.
  • the second spring seat 42 attached to the intermediate plate-side support arm 24 is configured so that a pair of the clamping protrusions 46 and 46 sandwich the attaching portion 24b, and the attachment strength is relatively low. Therefore, in the second spring seat 42, different operations are carried out according to the difference in the input positions from the coil springs 31 and 32. This difference in the input positions occurs due to the presence/absence of the displacement of the second spring seat 42 and the coil springs 31 and 32 in the device outer diameter direction.
  • the contact state between the coil springs 31 and 32 and the seat portion 43 is substantially uniform around the entire perimeter, and the input of the intermediate plate-side support arm 24 and the coil springs 31 and 32 is carried out in the vicinity of the spring central axis Sc.
  • the second spring seat 42 receives input from the coil springs 31 and 32 via the overhang portions 44, and the overhang portions 44 and the seat portions 43 are elastically deformed in the device axial direction, as illustrated in Figure 7C .
  • the second spring seat 42 is elastically deformed following the deformation of the seat portion 43 while maintaining a state of sandwiching the attaching portion 24b of the intermediate plate-side support arm 24, as illustrated in Figure 7C .
  • the contact pressure of the coil springs 31 and 32 and the device inner diameter side of the seat portion 43 becomes stronger at the time of this deformation of the coil springs 31 and 32 in the device outer diameter direction.
  • the overhang portions 44 are separated in the outer diameter direction from the input position from the coil springs 31 and 32, so an input that interposes the overhang portions 44 is less likely to occur.
  • the second spring seat 42 changes the inclination with respect to the intermediate plate-side support arm 24 while maintaining the shape of the clamping protrusions 46 and 46, as illustrated in Figure 7B .
  • the deformation amount of the coil springs 31 and 32 in the device axial direction is small, and the deformation amount of the overhang portions 44 is also small.
  • the strength of the clamping protrusions 46 and 46 are secured by the ribs 46a and 46a, and therefore the damage is less likely to occur thereto.
  • Figure 10A - Figure 10N respectively illustrate modified examples of the metallic core exposed portion 451a, and are front views when viewing the seat portion 43 in a direction along the spring central axis Sc.
  • the metallic core exposed portion 201 illustrated in Figure 10A is an example in which the width of the seat portion 43 in the radial direction is increased compared to that described in the first embodiment. Therefore, even if the coil springs 31 and 32 are relatively moved in the radial direction of the spring central axis Sc with respect to the seat portion 43, the wear of the resin portion is less likely to occur.
  • the metallic core exposed portion 202 illustrated in Figure 10B is provided in a position further on the device inner diameter direction side than the spring central axis Sc in the same way as in the first embodiment, and is provided divided into three parts in the circumferential direction, centered around the spring central axis Sc.
  • the metallic core exposed portion 203 illustrated in Figure 10C is a modified example of Figure 10B and an example in which the division is into two parts. Therefore, the same action and effect as the example illustrated in Figure 10B can be obtained.
  • Figure 10D is an example in which the metallic core exposed portion 204 is provided extended in the circumferential direction beyond the spring central axis Sc to the device outer diameter direction side.
  • Figure 10E - 10J are examples in which the metallic core exposed portions 205 - 209 are respectively provided in three locations at the height in the vicinity of the spring central axis Sc in the device radial direction and on the device inner diameter side.
  • the metallic core exposed portions 205 - 209 illustrated in Figure 10E - 10J have respectively different exposed shapes.
  • the metallic core exposed portions 205 of Figure 10E are configured to be rectangular.
  • the metallic core exposed portions 206 of Figure 10F are configured to be triangular.
  • the metallic core exposed portions 207 of Figure 10G are configured to be circular.
  • the metallic core exposed portions 208 illustrated in Figure 10H are respectively configured so that the sides close to the spring central axis Sc are rectangular and the sides far from the spring central axis Sc are circular.
  • the metallic core exposed portions 209 illustrated in Figure 10J are respectively configured so that the sides close to the spring central axis Sc are the upper bases and the sides far from the spring central axis Sc are the lower bases of an isosceles trapezoid.
  • the metallic core exposed portions 205 - 209 may be arranged as illustrated in Figure 10E - 10J . Therefore, it is possible to suppress wear of the resin portion by the metallic core exposed portions 205 - 209, and to maximally secure a low friction resistance portion of the coated region 43b by the resin while keeping the exposed portion of the seat portion metallic core member 451 at the minimum required area.
  • Figure 10K illustrates an example in which the metallic core exposed portions 210 are provided divided into five parts of the entire circumference surrounding the spring central axis Sc in the spring seating surface 43a, and in which a coated region 43b is provided to the device outermost diameter direction portion. That is, if the locations of the spring seating surface 43a with which the coil springs 31 and 32 come in strong contact and slide span over substantially the entire circumference, the metallic core exposed portions 210 can be divided and arranged in this manner. Therefore, it is possible to suppress wear of the resin portion by the metallic core exposed portions 210, and to maximally secure a low friction resistance portion of the coated region 43b by the resin while keeping the exposed portion of the seat portion metallic core member 451 at the minimum required area.
  • Figure 10M is an example in which the metallic core exposed portion 211 is divided and arranged in two locations of the spring seating surface 43a in the device outer diameter direction and the device inner diameter direction.
  • the metallic core exposed portions 211 may be provided in this manner. Therefore, it is possible to suppress wear of the resin portion by the metallic core exposed portion 211, and to maximally secure a low friction resistance portion of the coated region 43b by the resin while keeping the exposed portion of the seat portion metallic core member 451 at the minimum required.
  • Figure 10N is an example in which the metallic core exposed portion 212 is provided on the device outer diameter direction side of the spring seating surface 43a.
  • the metallic core exposed portions 212 it is possible to suppress wear of the resin portion and to suppress contact friction resistance with the coil springs 31 and 32 by the resin of the coated region 43b.
  • the damper device of the present invention is installed between the engine and the motor of a hybrid vehicle, but the device can be mounted on a vehicle other than a hybrid vehicle. In other words, the device may be provided between the engine and the transmission.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Springs (AREA)
  • Fluid-Damping Devices (AREA)
EP13893555.6A 2013-09-13 2013-09-13 Damper device Active EP3045769B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/074848 WO2015037126A1 (ja) 2013-09-13 2013-09-13 ダンパ装置

Publications (3)

Publication Number Publication Date
EP3045769A1 EP3045769A1 (en) 2016-07-20
EP3045769A4 EP3045769A4 (en) 2016-11-16
EP3045769B1 true EP3045769B1 (en) 2019-11-27

Family

ID=52665268

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13893555.6A Active EP3045769B1 (en) 2013-09-13 2013-09-13 Damper device

Country Status (8)

Country Link
US (1) US9926984B2 (ja)
EP (1) EP3045769B1 (ja)
JP (1) JP6028145B2 (ja)
CN (1) CN105556165B (ja)
MX (1) MX2016003225A (ja)
MY (1) MY173179A (ja)
RU (1) RU2639845C2 (ja)
WO (1) WO2015037126A1 (ja)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2636844C2 (ru) * 2013-09-13 2017-11-28 Ниссан Мотор Ко., Лтд. Демпфирующее устройство
WO2015037124A1 (ja) * 2013-09-13 2015-03-19 日産自動車株式会社 ダンパ装置
WO2019066030A1 (ja) * 2017-09-29 2019-04-04 アイシン・エィ・ダブリュ株式会社 ダンパ装置
KR102062876B1 (ko) * 2018-04-13 2020-01-06 이상욱 차량 현가장치용 코일스프링 지지대

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Publication number Priority date Publication date Assignee Title
DD130801B1 (de) * 1977-04-12 1979-08-29 Klaus Opelt Drehschwingungsdaempfer,insbesondere fuer kraftfahrzeugkupplungen
FR2637665A1 (fr) * 1988-10-07 1990-04-13 Valeo Dispositif amortisseur de torsion a fonctionnement silencieux
DE19544832C2 (de) * 1995-12-01 1998-01-22 Patentverwertung Ag Kupplung
JP2004183870A (ja) * 2002-12-06 2004-07-02 Exedy Corp スプリングシート、スプリング組立体
JP4925893B2 (ja) 2007-03-30 2012-05-09 日産自動車株式会社 スプリングシートおよびダンパーディスク組立体
JP4925894B2 (ja) * 2007-03-30 2012-05-09 日産自動車株式会社 スプリングシートおよびダンパーディスク組立体
DE102007033164A1 (de) * 2007-07-17 2009-01-22 Zf Friedrichshafen Ag Torsionsschwingungsdämpferanordnung
DE112009005530B4 (de) * 2008-07-24 2022-10-13 Exedy Corp. Dämpfungsmechanismus
JP5246297B2 (ja) * 2011-05-16 2013-07-24 日産自動車株式会社 サスペンション組み付け構造、スプリングシート、サスペンション組み付け方法
JP5203494B2 (ja) * 2011-10-18 2013-06-05 株式会社東郷製作所 ばねシート部材及びこれを具備するばね組立て体
DE102012220272A1 (de) * 2011-11-28 2013-05-29 Schaeffler Technologies AG & Co. KG Schwingungsdämpfer

Non-Patent Citations (1)

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None *

Also Published As

Publication number Publication date
WO2015037126A1 (ja) 2015-03-19
EP3045769A1 (en) 2016-07-20
CN105556165A (zh) 2016-05-04
EP3045769A4 (en) 2016-11-16
MY173179A (en) 2020-01-02
CN105556165B (zh) 2017-07-11
RU2639845C2 (ru) 2017-12-22
RU2016113837A (ru) 2017-10-18
MX2016003225A (es) 2016-06-07
JPWO2015037126A1 (ja) 2017-03-02
US20160223026A1 (en) 2016-08-04
JP6028145B2 (ja) 2016-11-16
US9926984B2 (en) 2018-03-27

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